Multiple-lever twenty-four-speed mechanism



Oct, 2,' 1928.

1,686,240 D. C. KLAUSMEYER MULTIPLE LEVER TWENTY-FOUR SPEED MECHANISM Filed July v, 1925 3 Sheets-Sheet 1 Suva/M01 W 634 MM D. C. KLAUSMEYER MULTIPLE LEVER TWENTY-FOUR SPEED MECHANISM Oct. 2,. 1928.

Filed July 7, 1925 3 Sheets-Sheet I 2 D. C. KLAUSMEYER MULTIPLE LEVER TWENTY- Oct. 2, 192 8.

FOUR SPEED mmcnmusm Filed July 1925 3 Sheets-Shea} 3 "EUT NEUTRAL .5 m 0. v w

cos speeds.

Patented 0a. 2, 1928.

DAVID C. KLAUSMEYER, OF CINCINNATI, OHIO, ASSIGNOR TO FORD TOOL COMPANY, OF

THE CINCINNATI BICK- CINCINNATI, OHIO, A CORPORATION OF OHIO.

MULTIPLE-LEVER TWENTY-FOUR-SPEED MECHANISM.

Application filed July 7, 1925. Serial No. 42,073.

This invention relates to machine-tools and it deals more particularly with improved means for giving to a suitably journaled member rotation at any one of a considerable number of speeds from a single speed in a prime-mover. The invention may be utilized for any one of many purposes in connection with machine-tools, such, for example, as for rotating the spindle of a drilling and tapping machine or for actuatin the spindle translating mechanism thereo For convenience, the invention will be shown and described in connection with the last-named mechanism but it is to be understood that this is merely one embodiment of the invention and that the invention also contemplates all of the various other uses for which a mechanism of this nature is adaptable.

The tool spindles of drilling and tapping machines are adapted to carry drills and taps of various diameters and inasmuch as each of these tools requires a different s eed of rotation and also a different rate of eed, for maximum efliciency, it is essential that means be provided for producing these vari- Also it is desirable that the means for producing these various speeds be simple in construction and that the means for effecting the various speeds be accessible to the operator and adapted readily to be manipulated, without confusion, to produce any desired speed.

In certain types of drilling and tapping machines, such for example, as the radial type in which all speed-change gears are carried in a tool-head translatably mounted on a radial arm, only very limited space is available for the various mechanisms. Heretofore certain mechanisms have been designed to produce the desired number of speed changes and adapted to be embodied in a radial drill head but these prior devices have usuallybeen more or less complicated and frequently include an actuating lever (or levers) movable to a lurality of positions in each of a plura ity of transverse lanes, thus the compound movements of said ltvers has led to confusion to the operator.

This invention has for an object to provide an improved multiple speed mechanism adapted to be embodied in the tool-head of a radial drilling and tapping machine and in which all of the speeds are produced by movement of onl two levers, each adapted to be moved only in a single plane.

Another object is to provide in a tool-head three serially arranged speed-change devices including shiftable and non-shiftable gears adapted to produce twenty-four speed changes and to shift said shiftable gears by means of only two levers each adapted to be moved 1n only a single plane. A still further object of this invention is to provide, in a multiple speed mechanism including shiftable gears, a plurality of rotatable cams for shifting certain ones of the slnftable gears, and to provide improved means for rotating said cams.

Other objects and advantages will be in part indicated in the following description and in part rendered apparent therefrom in connection with the annexed drawings.

To enable others skilled in the art so fully to apprehend the underl ing features hereof that'they may embo y the same in the various ways contemplated by this invention, drawings depicting .a preferred typical construction have been annexed as a part of this disclosure and, in such drawings, like characters of reference denote corresponding parts throughout all the views, of which 'Fig. l is a sectional development of the improved multiple speed mechanism as utilized to actuate a spindle feed mechanism. Fig. 2 is a plan of the mechanism illustrated in Fig. 1, with the parts in their normal 0 erative positions. Fig. 3 is a section substantially on the line 33 of Fig. I. Fig. 4 is a detail view showing means for throwing out the manual feed when the power feed is rendered effective to translate the spindle. Fig. 5 is a section on the line 5-5 of Fig. 4. Fig. 6 is a section on the line 6-6 of Fig. 1. Fig. 7 is a development of the gearshifting cams, the intermediate cam being shown as shifted approximately 180 degrees .to-bring the starting point of all of the cams in the same vertical line more clearly to illustrate the functioning of the cams. Fi 8 is a diagrammatic view illustrating the ow of motion through the three serially arranged sets of change gears, selectively to produce any one of twenty-four speeds.

Referring more particularly to the drawings, the invention is illustrated as embodied in a spindle feed mechanism for drilling machines, by means of which the spindle may be fed lengthwise at any one of a plurality of speeds to cause the tool carried thereby to enter and emerge from the work; the rate of feed being determined by thesize and type of tool being used and the nature of the work bein operated on. In the drawings S designated the spindle formed in its lower end with a socket an adapted to receive any one of the tools commonly used in this type of machine tool. Any suitable means may be employed to rotate the spindle and inasmuch as the spindle rotating means forms no part of this invention illustration and description thereof is deemed unnecessary.

During the rotation necessary that the spindle be moved lengthwise for purposes hereinbefore described. This may be efiected by having the spindle rotatably but non-translatably journaled in a sleeve 1 provided with a rack 2 with which meshes an actuating pinion 3 secured upon a shaft 4 journaled transversely to the spindle. A worm-wheel 5, also secured upon the shaft 4, is driven by a worm 6 fixed upon a power delivery shaft 7 adapted selectively to be rotated at any one of a plurality of speeds by means later to be described.

Power to actuate the spindle feed mechanism maybe provided by any suitable primemover, such for example, as a gear P secured upon a suitable spindle driving sleeve D. Power from the prime-mover flows to the power delivery shaft through three separate speed change mechanisms A, B and C affording respectively two, four and three speed changes which together render available twenty-four speeds in the power delivery shaft. The speed change device A includes a gear-unit 8 splined upon a shaft 9 'journaled parallel with the spindle and adapted to be driven from the gear P through a gear 10 fixed to' said shaft, and permanently in mesh with said gear P. The gear-unit 8 provides gears a and 6 adapted selectively to be meshed with gears 0 and d, respectively, provided by a gear unit 11 rotatably journaled on a shaft 12 parallel with the shaft 9.

The speed change device B comprises gears 0, e, f and 9 provided by the gear-unit 11 and gears h and jlc provided by gear units 13 and 14 splined upon a sleeve 15 rotatablyjournaled onthe power delivery shaft 7. The sleeve 15 carries a gear L constituting the initial gear of the speed change device C. This gearis maintained permanently in mesh with a'gear m provided by a gearunit 16, rotatably journaled on the shaft 12, and is also adapted to be engaged by a clutch element at provided by a shiftable gear-unit 17 splined to the power-delivery shaft 7. The gear-unit 16 also provides a gear 1,) adapted to be meshed with a gear 79 forming a part of the gear-unit 17. A gear q is rotatably journaled on the shaft 12 and is adapted to be meshed with a gear 1' provided by the. gear unit 17. The gear q is, in effect, a part of the gear-unit 16 and may be made integral therewith, but, for convenience of manufacture 'means of clutch elements of the spindle, it is and assembling, it preferably is made as a separate part and connected therewith by s and t. Means, later to be described, is provided for shifting the gear-units 8, 13, 14 and 17 selective to produce any one of twenty-four speeds in the power delivery shaft from a single speed in the rime-mover. The scheme of the transmission and the various gear settings to produce any desired speed in the power delivery shaft will be clearly understood by referring to Fig. 8. The single speed in the shaft 9 passes through the speed change device A either through gears a and c or b and cl thus delivering two speeds to the device B. Likewise these speeds are multiplied by four in the device B by causing the power selectively to flow through gears ch, e-e', fj or 9-70, thus delivering eight speeds to the-speed change device C. These eight speeds are further "multiplied into twenty-four speeds by the speed-change device C, by selectively meshing the gears there- 'of so that power may flow through any one of the three courses now to be described. By shifting the gear-unit 17 upwardly so as to engage it directly with the sleeve 15 power will be caused to flow through gear L and clutch n carried by the gear-unit 17 splined to the power delivery shaft thus delivering to the shaft 7 the eight speeds produced by the devices A and B. Eight additional speeds may be obtained through gears L, m, 0 and p. Still another eight speeds are available through gears L, m, (7 and 7'.

The gear-unit 17 of the speed-change device C, is adapted selectively to be shiftedto any one of its three operative positions by a shifter 28 translatably mounted on a rod 32 secured in a stationary framework 22. One end of the shifter 28 engages an annular groove 27 in the gear-unit 17 and the other end is forked and engages a reduced portion 26 of a collar 25 fixed to a shaft 24 rotatably and translatably journaled in the'stationary framework 22. Endwise movement effected by a lever 23 fixed u journaled in bearings provide on a shaft 21 by the stationary framework. A yoke 20 fixed to the shaft 21 engages a collar 19, fixed to the shaft 24 and thus the swinging movement of the lever 23 about the axis of the shaft 21 moves the shaft '24 endwise and the gear-unit 17 is shifted axially on theshaft 7. A yielding detent 18 is adapted to engage notches L, 0 and in the shaft 24 when the gear-unit 17 is in position to engage the gears L, o and 9, respectively. A similar notch Z cooperates with the detent 18 to maintain the gear-unit 17 in its neutral position, that is with the gears p and 0" intermediate the gears 0 and 9 when it is desired to render the power feed inefiective.

of the shaft 24 is I he gear-unit 8 is engaged by a shifter 28 translatably mounted on a shaft 29 carried by the stationary frame. The gear-units 13 and 14 are engaged by shifters 30 and 31, respectively, likewise translatably mounted on the rod 32. The shifters 28*; 30 and 31 carry studs or rollers 28, 30 and 31 respectively, which track cam-grooves 33, 34 and 35 formed in a rotatable cam cylinder 36. The cam grooves 34 and 35 are endless and extend continuously about the periphery of the camcylinder but the cam-groove 33 is provided with closed ends and extends one and seventenths about the cam-cylinder. The camcylinder 36 is rotatably journaled in the framework 22 and has a splined connection with the shaft 24 whereby the cam may be rotated by the shaft and the shaft may be translated independentl of the cam to effect shifting of the gear-unit 17. In Fig. 1 the cam-cylinder is shown in full lines at the right of the figure and in dotted lines at the left thereof, more clearly to show the connection between the shifter 28 and its actuating cam-groove 33. It will readily be perceived that rotation of the cam-cylinder 36 will, through the cam grooves, cause the shifters 28", 30 and 31 to be translated thereby shifting the gear-units so to mesh the gears as to produce any one of the available speeds. The shifters are preferably formed with bifurcated ends 28', 30 and 31 respectively, which embrace the cam-cylinder and prevent rotation of the shifters about their supporting shafts. By guiding the shifters adjacent the point where the power is applied and close to the supporting shafts the shifters also are prevented from binding on their supports and are therefore maintained freely translatable thereon.

The shaft 24, and the cam-cylinder 36 splined thereto, may be rotated by means of a lever 37 fixed to a segment 38 fulcrumed on a cylindrical boss 50 on a cap 51 secured to the framework 22. The segment 38 is provided with a toothed portion 39 which meshes with a gear 40 forming a part of a gear-unit 41 having a trunnion 42 journaled in a bushing 43 supported by the framework. A gear 44 also forms a part of the gear-unit 41 and this gear meshes with a gear 45 provided by a sleeve 46 splined to the lower end of the shaft 24.

Thus it will be seen that movement of the lever 37 about the boss (which has its axis in line with the axis of the shaft 7) will effect rotation of the shaft 24 and the cam-cylinder 36. The pitch radii of the segment 39 and the gears 40, 44 and 45 are such that a movement of the lever 33 of approximately 120 degrees efi'ects one and seven-tenths rotation of the cam-cylinder 36 for purposes later to be explained. The cap 51 forms an enclosure for the segment 38 and the gears 40, 44 and 45 and it also serves as a support for a stub-shaft 47 which carries a hand-wheel 48 forming a part of a hand-feed for the spindle later to be described.

The lever 37 projects through a slot 49 positions of the lever 23 in combination with each of the eight operative positions of the lever 37. The indicator for the speed change device C may consist of a pointer 54 movable with the lever 23 and adapted to cooperate with indicia on a suitable index-plate 55 secured to stationary framework 22 adjacent said pointer.

Referring to Fig. 2, it will be seen that the pin 28 enters its cam-groove 33 at the ammetrically opposite side of the cam cylinder from the pins 30* and 31 and therefore it is to be understood that the starting point of the cam groove 33 is 180 degrees from the starting point of the grooves 34 and 35. For the purpose of more clearly setting forth the coordination and functioning of the cams, in Fig. 7 the cam 33 is shown as shifted 180 degrees about the cam cylinder to bring the starting points of all of the cams on the same vertical line.

Referring now to Fig. 7 in which the entire cam cylinder is shown developed and for convenience of description is shown as divided into ten equal divisions, the starting points of the cams, 33, 34 and 35 are indicated by 33 34 and 35 respectively.

The lever 37 is adapted to be moved horizontally about 120 degrees and this motion,

through the segment 39 and gears 40, 44 and gears of the devices A and B will be as follows: The-pin 28 is now in the lowermost eflective run 33 of the cam 33 and therefore the gear I) is in engagement with the gear d, (which engagement it maintains for eighttenths of a rotation of the cam-cylinder, or until the pin 28* reaches the point 33' of the cam 33). The pins 3O" and 31 are in the neutral portions of the cam grooves 34 and 35 respectively. A one-tenth rotation of the cam-cylinder causes the cam groove 35 to shift the stud 31 to the position 35" which causes the gear unit 14 to be shifted downwardly to mesh the gears g and k thereby effecting a drive through the speed change devices A and B through gears bdg-k (see Fig. 8). A further two-tenths rotation of the cam c 31 to be shifted through the neutral position 35 to the effective point 35 which causes the gear unit 14 to be shifted upwardly and effecting a drive through bclf-j. It is to be noted that during this movement the stud 28" continues to track the lower effective run 33 and the stud 30 is tracking a neutral portion of the came groove. 34. A further two-tenths rotation of the cam-cylinder shifts the stud 31 through the position 35 (which causes the gear unit 14 to be shifted to its neutral position) and the stud 30" is moved to the position 34 in the cam groove 34 thereby shifting the gearunit 13 downwardly and effecting a drive through the gears b-dez'. Another twotenths rotation of the cam-cylinder shifts the stud. 30 through the neutral position 34 in the cam groove 34 to the position 34, thereby shifting the gear-unit 13 upwardly, engaging the gears ch and effecting a drive through gears bd 0-h. A further threetenthsrotation of the cam shifts the stud 34 through the neutral portion 34 of the cam 34 and shifts the stud 28 from the effective run 33, through the neutral point 33, and into the upper effective run 33, thereby shifting the gear-unit 13 to its neutral position and shifting the gear-unit 8 upwardly to mesh the gears a and 0.

It is to be observed that the cam cylinder has now received one complete rotation and the cam grooves 34 and 35 have each performed its complete operation, that is successively to shift the gear units 13 and 14, respectively, to their two operative positions, while the portion 33 of the cam groove 33 maintained the gears b and d in mesh, thereby combining the four speed changes afforded by the speed device B with the gearsb and d of the device A. The stud 28 also has been shifted to the upper effective run 33 and in a further seven-tenths rotation of the cam cylinder the cam grooves 35 and 34 will again shift the studs 31 and 30 respectively, as previously described, again to cause gear units 14 and 13 p each again to be shifted to its two effective positions; thus during this last seven-tenths rotation the gears g-k, fj, e-z', and 0-72, are successively combined with" the gears a and 0 and four more speeds are provided. This last seven-tenths rotation of the cam cylinder brings the studs 30 and 31 to the points 34 and 35 in the cam grooves 34 and 35, respectively, and the stud 28 contacts with the closed end 33 of the cam groove 33 thus preventing further rotation of the cam cylinder and thereby preventing further movement 0 the lever 37.

Each of the eight speeds provided by the linder will then cause the stud speed change devices A and B may be multiplied by three in the device C by moving the lever 23 thus producing the twenty-four speed hereinbefore described.

In addition to the hereinbefore described power drive for the worm 6, means also is provided whereby the worm may be rotated manually and this manual drive is so coordinated with the power drive that they both may not be effective at the same time. This is ac-- complished by providing automatically acting means to hold the manual means out of action whenever the power feed is effective and to connect the manual means when the power'feed is thrown out of action. To that end a clutch element 56 is fixed to the shaft 7 and this clutch element is adapted, at certain times, to be engaged by a similar clutch element 57 splined to the shaft 47. Fulcrumed upon a pin 58 held in the stationary frame work is a three-arm lever 59 of which one arm 59 is connected with the clutch element 57. Another arm 59 engages a pin 60 slidingly fitted in a bore 61 in the frame 22 and provided with a conical end adapted to en age an annular groove 62 in the shaft 24. he roove 62 is so located that the pin 60 engages 1t only when the gear unit 17 is in its neutral position and therefore only when the power feed is inoperative. A spring plunger 63, within an arm 59 of the lever 59, bears against the stationary frame and causes the lever to be swung about the pin 58 when the groove 62 is aligned with the in 60 thereby shiftin the clutch element 5 into engagement wit the clutch element 56. As the power feed is again rendered effective by axial movement of the shaft 24 the inclined walls of the groove 62 act upon the conical end of the pin 60 and cause it to be pushed outwardly against the arm 59 which swings the lever 59 clockwise as viewed in Fig. 4 and thereby disconnects the clutch elements 56 and 57 thus rendering the manual feed ineffective.

From the foregoing it will be perceived that this invention provides simple and efficient means for producing as many as twenty-four s eed changes and that all of said speed c anges may be effected by shifting only two levers each of which moves only in a single lane and in only a small fraction of a rotation in said lane.

Without urther analysis, the foregoing will so fully reveal the gist of this invention that others can, by applying current knowledge, readily adapt it for various utilizations the generic or specific aspects of this invention and, therefore, such adaptations should be, and are intended to be, comprehended within f the meaning and range of equivalency of the following claims Having thus revealed this invention, I

rime mover with said shaft to rotate the atter at a plurality of speeds; a rotatably and translatablly mounted shaft connected to control said t ree speed-change devices; means to rotate said shaft to cause it to actuate two of said speed-change devices, and means to translate said shaft to cause it to actuate one of said speed-change devices.

2. A multiple speed mechanism combining a prime mover; a shaft; three s eed-change devices, each including shiftab e and nonshiftable gears, operatively connecting said prime mover with said shaft to rotate said shaft at a plurality of s eeds; rotatable cams connected to shift the s iftable gears of two of said speed-change devices; atranslatable member adapted to shift the shiftable gears of the third speed-change device; a shaft connected to rotate said cams and to translate said member; and means to rotate and translate said shaft.

3. A multiple speed mechanism combining a plurality of speed-change devices each including shiftable and non-shiftable gears; rotatable cams connected to shift the shiftable gears of two of said devices; a member adapted to shift the shiftable gears of another of said devices; a single lever movable in a single plane, 0 eratively connected to rotate said cams; an another lever, movable in a single plane, operatively connected to shift said member.

4. A multiple speed mechanism combining a plurality of speed-change devices each including shiftable and non-shiftable gears;

rotatable cams connected to shift the shiftable gears of two of said devices; a translatable shifter adapted to shift the shiftable gears of another of said devices; a rotatable and translatable member translatably and non-rotatably connected with said cams and rotatably and non-translatably connected with said shifter; and means selectively to rotate and translate said member to effect rotation of said cams and translation of said shifter.

5. A multiple speed mechanism combining a plurality of speed-change devices each including shiftable and non-shiftable gears; a rotatable cam connected to shift the shiftable gears of one of said devices; a translatable shifter adapted to shift the shiftable gears of another of said devices; a rotatable and translatable member translatably and non-rotatably connected with said cam and rotatably and non-translatably connected with said shifter; a lever connected with said member to shift said member axially to cause it to shift the gears of one of said devices; and a lever connected withsaid member to rotate said member to cause it to rotate said cam thereby to shift the gears of another of said members. 1

6; A multiple speed mechanism combining a plurality of serially arranged speed-change devices each including shiftable and nonshiftable gears; gear-shifters engaging said shiftable gears; rotatable cams adapted to move certain ones ofsa-id gear-shifters;ashaft to which said cams are translatably and nonrotatably secured; a first lever connected to translate said shaft, means actuated by the translation of said shaft to shift one of said gear shifters and the gears controlled thereby; a second lever fulcrumed on an axis substantially parallel with the axis of said shaft and movable only in a single plane; and a motion multiplying connection between said lever and said shaft to give to said shaft and cams one and a fraction rotations by a partial rotation of said lever.

7 In amachine tool having a prime mover and a power delivery shaft, a multiple speed mechanism including, in combination a plurality of speed-change devices each including shiftable and non-shiftable gears, operatively connecting said prime mover with said power delivery shaft, to give to the latter a plurality of speeds from the former; a rotatable cam; a gear-shifter actuated by said cam and connected to shift the shiftable gears of one of said devices; a rotatable and translatable shaft having a spline connection with said cam; a gear shifter connected with said shaft and adapted in the translatory movement of said shaft. to shift the shiftable gears of another of said devices: means including a lever connected with said last-named shaft to translate said shaft and the gear shifter connected therewith, means independent of the shaft translating means to rotate said shaft and said cam,.said last named means including a gear splined to said shaft: a lever movable in a single plane; and a multiple gear connection between said lever and said splinedgear.

8. A multiple speed mechanism combining a plurality of speed-change devices each including shiftable and non-shiftable gears; a rotatable cam connected to shift the shiftable gears of one of said devices; a translatable with each of said means to indicate the speed produced by the combined positions of said evers. v I

9. In a power transmitting mechanism including a prime mover and a power delivery shaft, in combination, a pluralit of speed change devices, each including shlftable and non-shiftable gears, operatively connecting said prime mover with said shaft; a rotatable camoperatively connected to shift the shiftable gears of one of said devices; a shaft translatably and non-rotatably connected with said cam; a gear translatably and nonrotatably mounted on said shaft; means to translate said shaft; means actuated by the translation of said shaft to shift the gears of said speed change devices; a gear-segment; a gear-connection between said segment and said last-named gear; and a lever connected with said segment and adapted through said gear-segment and gear-connection to rotate.- said cam-shaft and cam thereby to shift the gears of one of said speed change devices.

10. A multiple speed mechanism combinin a prime-mover; a driven member; a plurality of speed-change devices connecting said prime-mover with said driven member to rotate the latter at a lurality of speeds; a rotatably and translatab iy mounted shaft connected to control all of said s eed-change devices; means to rotate said s aft to cause it to actuate one of said speed change devices; and other means to translate said shaft to cause it to actuate another of said speed change devices.

11. A multiple speed mechanism combinin a prime-mover; a driven member; a plurality of speed-change devices connecting said prime-mover with said driven member to. rotate-the latter at a plurality of speeds; a rotatably and translatably mounted shaft connected to control said speed-change devices; a lever movable in a single plane and operatively connected with said shaft and adapted to translate it to cause it to actuate one of said speed change devices; a second lever movable in a single plane and operatively connected with said shaft and adapted to rotate it to cause it to acuate another of said speed change devices.

12. A multiple speed mechanism combining a prime-mover; a power delivery shaft; a plurality of speed-change devices operatively connecting said prime-mover and said shaft; actuating means for said speed change devices including a speed control shaft movable axially to effect one speed change device and movable angularly to effect another of said speed change devices; means to rotate and translate said control shaft; manual means to rotate said power delivery shaft; and means actuated by one of the movements of said control shaft to render ineffective said manual means.

13. In-a multiple speed mechanism includshiftable and non-shiftable gears, a pluralit of gear-shifters each operatively connecte with one of said shiftable gears; a shaft with which oneof said gearshifters 1s connected;'means to translate and ing a plurality of to rotate said shaft; a rotatable cam opera- .each of said cams being connected to actuate one of said gear-shifters and each adapted, throu h its co-operating gear-shifter to move one 0 said gear-units, to two operative positions in one com lete rotation of the cam to produce some 0 the available speeds, the fractional rotation serving to produce the remaining speeds, said cams being so co-ordinated that the one and a fraction rotations causes one of said cams to perform its entire function twice while the other cam performs its entire function only once.

15. A multiplespeed mechanism comprising a prime-mover; a power delivery shaft; a plurality of relatively shiftable gear-units operatively connecting said prime-mover with said power-delivery shaft; a shifter engaging each of the shiftable gear-units; means to actuate certain of said shifters, said means including a rotatable cam cylinder provided with a continuous cam groove and a cam groove extending one and a fraction about the periphery of said cylinder, each of said cam grooves being adapted through one of said shifters to move one of said gear-units to a plurality of positions in one rotation of said cylinder; an actuating element; means to limit the movement of said element to less than a complete rotation; and a motion multiplying connection between said element and said cam cylinder, to give to said 0 linder more than a complete rotation by the imited movement of said lever, said cam grooves being so constructed and arranged that one cam performs its complete action twice to a single actuation of said actuating element while the other performs its complete action only once.

16. A multiple speed mechanism comprising a prime-mover; a power delivery shaft;

a plurality of relatively shiftable gear-units operatively connecting said prime-mover with said power delivery shaft; a shifter engaging each of the shiftable gear-units;

three synchronously rotatable cams of which said shifters to two operative positions successively to engage certain of said gear-units; means to give to said rotations; and means to arrest therotation of the cams, said cams being so co-ordinated that in the said one and a fraction rotations two of said cams each moves one of said shifters to its two operative positions twice while the other cam moves its co-opera-ting shifter to its operative positions only once.

17 A multiple speed mechanism comprising a prime-mover; a power delivery shaft;

change gears operatively connecting said I prime-mover with said shaft, said change cams one and a fraction gears including a plurality of shiftable gearunits; shifters operatively connected with said gear-units; rotatable cams for operating certain of said shifters; a member 0 ratively connected with another of said 'fters; a driving connection between said member and said cams; means to translate said member to cause it to move the last named shifter; and means to rotate said member to cause rotation of said cams.

In witness whereof, I have hereunto subscribed my name.

DAVID C. KLAUSMEYER. 

